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US2444886A - Screw and nut actuating mechanism - Google Patents

Screw and nut actuating mechanism Download PDF

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Publication number
US2444886A
US2444886A US58724645A US2444886A US 2444886 A US2444886 A US 2444886A US 58724645 A US58724645 A US 58724645A US 2444886 A US2444886 A US 2444886A
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Prior art keywords
balls
screw
load
direction
nut
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Theodore W Vickers
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Theodore W Vickers
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20Screw mechanisms
    • F16H25/22Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20Screw mechanisms
    • F16H2025/2062Arrangements for driving the actuator
    • F16H2025/2075Coaxial drive motors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20Screw mechanisms
    • F16H2025/2062Arrangements for driving the actuator
    • F16H2025/2087Arrangements for driving the actuator using planetary gears
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20Screw mechanisms
    • F16H25/22Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H25/2214Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with elements for guiding the circulating balls
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H25/00Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20Screw mechanisms
    • F16H25/24Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454Brakes; Rotational locks
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00Metal working
    • Y10T29/49Method of mechanical manufacture
    • Y10T29/49826Assembling or joining
    • Y10T29/4984Retaining clearance for motion between assembled parts
    • Y10T29/49845Retaining clearance for motion between assembled parts by deforming interlock
    • Y10T29/49853Retaining clearance for motion between assembled parts by deforming interlock of sphere, i.e., ball, in socket
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/18Mechanical movements
    • Y10T74/18568Reciprocating or oscillating to or from alternating rotary
    • Y10T74/18576Reciprocating or oscillating to or from alternating rotary including screw and nut
    • Y10T74/18704Means to selectively lock or retard screw or nut
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/19Gearing
    • Y10T74/19642Directly cooperating gears
    • Y10T74/19698Spiral
    • Y10T74/19702Screw and nut
    • Y10T74/19744Rolling element engaging thread
    • Y10T74/19749Recirculating rolling elements
    • Y10T74/19767Return path geometry
    • Y10T74/19772Rolling element deflector

Description

July 6, 1948, T. w. vlcKERs SCREW AND NUT ACTUATING MECHANISM 3 Sheets-Sheet 1 Filed April 9 1945 @www N mm E am .E Y mm M x N mw T. w. vlcKERs 2,444,886

SCREW AND NUT ACTUATING MECHANISM 3 sheets-Sheet 2 July 6, 1948.

Filed April?, 1945 ATTORNEY Plantea Julye, `194e. l. l 2,444,886

\ UNITED uSTATES PATENT OFFICE v 2,444,886 l SCREW AND NUT ACTUATING MECHANISM Theodore W. Vickers, Los Angeles, Calif.`

Application April 9, 1945, Serial No. 581,246 12 Claims. (Cl. 'I4-459) This'invention relates generally to mechanical direction wherein they are caused to feed through movements and more particularly to actuating the screw and nut grooves by pressure of 'the mechanisms such as screw and nut operated load, so that in order for the load to driveA the mechanisms employed in aircraft actuators, liftmechanism, the balls will be forced to slide rather ing jacks, vises, presses and other screw devices o than roll in the grooves, wlththe resulting greatly by which an applied force is greatly multiplied increased friction between the screw and nut beat 'a load. ing suilicient to support the load.

Although actuating mechanisms such as the It is a further object of this invention to proscrew and nut, and worm and gear have a highA vide a mechanism of the above described characmechanical advantage,` the sliding friction bel ter, which, in its application to an aircraft actuatween the threads or teeth of the screw and tor or other device subjected to a load in two those of the nut or gear is very great, thus makopposed directions, will be automatically operable ing such mechanical movements extremely into obstruct rolling movement of the balls in the eilicient because of the relatively large frictional grooves of the screw and nut in one direction or loss. To reduce this friction to a relatively small l the other according as the load is imposed upon amount, a mechanism known as the ball bearing the mechanism to drive same in one direction screw nut has been developed and employs a or the other, so that the sliding friction thus proseries of balls in'place of screw threads, which vided between the screw and nut will support the balls are forced to roll in mating helical grooves load, all while enabling the driving force to accr races in the screw and nut, by load pressure 2o 'cuate the mechanism in either direction in cpimposed thereon when working, and are byposition to the load with the balls Vfree to roll and passed from the grooves through the nm, and thus reduce the friction between the screw and returned to the grooves so as to circulate freely nut for high efficiency operation of the mechin one direction or the other according as relaanism.

tive axial movement of the screw and nui; in one It is a still further object of this invention to direction or the other is effected under load'. provide a control means for a. nut and screw or This ball bearing screw nut mechanism elimisimilar actuating mechanism by Wlllell n lenates the thread-sliding friction by substitutingstrleted Circulation may be effected under the therefor the rolling friction of the balls, thus pressure 0f a load in excess of a predetermined vastly increasing the efnciency of the mechanism maximum 10nd immevably Slipperted by the while retaining its 'mechanical advantage. mechanism, so as to compensate for sudden or However, this ball bearing nut mechanism has heavy load shocks which might otherwise impose the disadvantagethat upon removal of the drivdemeglng Crushing StreSSeS 0n the bellS- AlSO,

ing force therefrom, the load will act through the load can be rendered free to drive the mechtheballs to drive the mechanism in a retrograde ansm and thus move at a predetermined rate direction because of the lack of friction between upon removal of the driving force from the mechthe screw and nut. To prevent such overhau enSIn, all t0 the end 0f greatly extending the A of the mechanism, a holding force must be conrange of use of the mechanism. I

tinuously applied thereto, `or g, braking device With these and other objects in view, the inprovided in order to support the load. 40 vention resides in the combinations, arrange- The primary object of this. invention is to proments and functional relationships of elements vide a, ball bearing screw nut mechanism or simias set forth in the following specification and positive means by which the driving of such In the accompanying drawings,

mechanism in a retrograde direction by the load Figure 1 is a longitudinal sectional view of an is prevented by interposing sufficient sliding fricaircraft actuator, with one form `of mechanism tion between the screw and nut for the load to embodying this invention, applied thereto and be supported without the use of a holding force, occupying one active position;

braking, or other extraneous device. Figure 2 is an enlarged fragmentary longitudi- Morespecifically, it isan object of this invennal sectional view showing a portion of the airtion to provide a ball bearing screw nut or simicraft actuator with the mechanism embodying lar actuating mechanism embodying means by this inventionv occupying another active position;

by the load is prevented by stopping the relatively views taken, respectively, on the lines 3 3, 4-4 frictionless rolling movement of the balls in the and 5-5 of Figure 2;

lar actuating mechanism embodying simple and particularly pointed 011i? ln the appended Claims.

which the retrograde drivingof such-mechanism Figures 3, 4 and 5 are' transverse sectional Figure 6 is a vertical longitudinal sectional tween the elements s and N which is nlled with view of a lifting Jack with another form of mecha series of hardened steel balls Il providing an anism embodying this invention applied thereto; operative connection between the elements which and functions in the manner oi a screw thread to Figure 7 is a transverse sectional view taken 5 relatively feed the elements axially 1n response on the line 1-1 of Figure 6. torotation of the screw element S.

Referring specifically to the drawings, and When the screw element 8 is being driven in illustration, embodied in an aircraft actuator 10 the attaching eyes Il and Il, or move them a screw element S. thus obtained with a minimum frictional loss. The screw element S is in the form of a shaft as the balls provide relatively small rolling fric- |2, one end of which is iournaled in the casing tion between the screw and nut elements, rather Il is adapted to be driven in one direction or ball bearing screw nut mechanism has the disthe other by a reversible electric motor M whose advantage that the load being moved will as field Il is supported in the casing, and whose readily drive the mechanism in a retrograde div armature Il and commutator I1 are fixed on a rection by overcoming the slight rolling friction tubular shaft I8 freely receiving the shaft lo in of the balls, upon removal of the driving force co-axial relation thereto, and Journaled in bearfrom the mechanism, thus rendering saine4 inings Il and 2li supported by plates 2| and 22 capable of immovably su the load in the shafts 2s and mesh with a large gear 21 fixed of the load, all of Awhich adds ally to the to the shaft to the end of providing a speedcost and upkeep of the mechanism, reducing gear train between the armature shaft o overcome the disadvantage this invention eans at a slow speed relative to that of the motor M. preferably co-eeiing directly with the balls l0 The nut element N is composed of two secand comprisingin one embodiment, pawls or dogs tions and 2i. the section 30 being in the form 30 and DiVOtil-llv mvllnted by RTCW! 2 and of a cylindrical body havinga longitudinal bore I3 0n the plate l1 at opposite sides of the ball I2 of a slightly larger diameter than that of the 4U Conduit i., and urged by springs Il and t0 ceiving the shaft is, whose outer end is Jour- The pawls are disposed in opposed relationship posed and alined relation to the attaching eye are required 1n the use 0f the invention on an The section 30 is mounted between the heads a load imposed thereon sometimes in one di- 34 and 35 by anti-friction bearings I0 and 4| rection, and Bt other time# 111 the 099081150 difor axial movement with the section. as a reiion single unit, and is provided with keys 42 co-act 55 Cil-acting with the respective pawls III and 0| con a lost motion rotational driving connection (Fignection provided between thev sections 2| and ure 3) between the sections 30 and 3| for a pur- 3| of the nut element N by the keys 42 and keypose to be later described. ways 43, are actuating lugs in the form of pins The wall oi the bore 32 in the section 30 of 60 10 and 1| projecting from the barrel Il o! the the nut element N is provided with a helical section 2| for actuation of the respective pawls The ends of the groove 50 are closed on' from 65 the section It tends to rotate relative to the the ends of the section 30 by two opposite] section 2| in one direction or the other in the sitioned ring segments 52 and 53 seating tightly operation of the invention which is as follows in the groove so as to provide a plurality of inith one o e eyes and Il anchored to volutions communicate at the ring segments 52 7o moved in adirection separating the eyes. the

posed ball conduit Il formed in plate -51 secured direction of the arrow in Figure 1. thus tending by screws la on a dat face of the section 3o, all to cause the balls 5l to circulate through the ball to the end of providing a continuous ball race berace in the direction of the arrow. It will be shown in Figure 2 by the arrow in Figure by the driving force. This,

noted that under this. condition. the pawl ll has been moved by. the pin Il to its inactive position. whereas the pawl il is freed of itspin 1l so as to be yleldingly urged by its spring et to its active position, all during the initial slight rotation of the section 3l relative tothe section Il permitted by the lost motion driving connection between the keys 42 and keyways u, following which the nut element N will be moved to the right in Figure l as the balls freely click past the bill of the active pawl ll in the direction of the arrow, under the pressure imposed by the driving force on those balls in the grooves l and il. Therefore, it will be evident that the high mechanical advantage of the screw and nut will be obtained, with an attending high emciency duetothe negligible rolling friction provided by the ballsbetween the screw and nut elements.

^ lHowever. upon removing the driving force from the screw element S the pressure imposed on the balls in the grooves l0 and Il by the resistance f of the load, will be reversed, thus tending to circulate the balls in the direction reverse to the arrow, which circulation is positively prevented by the active pawl Il. As the tendency of the nut element N to rotate the screw element S in a retrograde direction. is resisted by the large sliding friction of the now non-circulating balls between the elements, rather than the small rolling friction present when the driving force was applied, the load will be supported in the position to which it has been moved.

Assuming that the loadcondition is reversed and acts in the opposite direction by tending to separate the eyes Il and 39, the pawls CII and Il will be reversed automatically to `the positions the slight initial` reverse rotation of the element Il permitted by the lost motion driving connection between the keys 42 and keyways so that in response to driving the nut element N in the direction opposite to A 1 -to feed the nut element towards the left, the balls Il will circulate in the direction of thearrow in Figure 2 by freely clicking past the now active pawl Il. Upon removing the driving force from the screw element, the reverse circulation. ofthe balls by the load will be prevented bythe pawl Il withthe advantages above described.

It will be noted that the bills of the pawls 60 and 8l can .be so shaped as to permit a restricted circulation of the balls by sudden or heavy loads in excess of a predetermined maximum load, so as to prevent damaging'crushing stresses from being imposed on the balls by such-excessive loads, all without adversely affecting the functioning of the balls in co-action with the pawls to support loads up to the predetermined maximum.

^ Furthermore, springs of; different strengths could be utilized for this purpose in order to compensate for excessive load shocks. Considering that surface of the pawl being engaged by theballs, as an inclined plane or a cam, it will be appreciated that by reducing to ra predetermined inclined plane, the angle of the surface of the active pawl whichis being engaged by the balls to stop their circulation by l such surface bythe balls will be effected, so as to tendV to move the pawl` to inactive position against the pawl spring, which latter, under such condition is made of such strength to inefiectively oppose movement'of the pawl to inactive position bythe balls, and thus permit them to continue to roll but not so freely as in the direction caused in effect. is a brake a suitable crank handle l to be attached to drive the screw element through `the screw element S',

placed upon the flow' of the balls through the bypass, and thus a brake-on the "overha of the screw nut.

It will be clear from the foregoing description that regardless of whether the screw element S is being driven in one direction or oppositiorrto a load, the negligible rolling friction of the b; lls Si will be utilized, and that upon removal of the driving force, one pawl or. the other will automatically co-act with the balls to substitute the sliding friction for the rolling friction thereof in order to support the "load,

Reference will now be had to Figures v6 and I in which is illustrated a second `embodiment of this invention which can be applied to the lifting jack shown, or to a vise. press, or other device in which the load always acts in one direction.

The lifting jack comprises a base Il having a tubular standard Il in which is vertically slidable a plunger 82 havinga load-engaging head Il, and being secured to a nut element N co-acting with a screw element S'. The screw element is'in the form of a cylindrical shaft 84 rotatably mounted in the standard by a thrust bearing 'IB and a central retaining screw 86. Fixed to the screw element is a relatively large gear l'l with which meshes a pinion gear 88 journaled inthe 'standard 8l and having a non-circular shank 89 to which (not shown) is adapted the gears.

The longitudinal bore l32a of the nut element,

N' is of a slightly larger diameter than that of and is provided with a helical groove Na co-acting with a' mating helical groove ila in the portion of the screw element which is adapted to be traveled upon by the nut element. The ends of the groove lila are closed oi from the ends of the nut element by two oppositely positioned ring segments 52a and a seating tightly in the groove so as to provide a plurality of intervening convolutions. The ends of these vconvlolutions communicate at the ring segments with tangential ball conduits a and lla in the nut element N', connected by an obliquely disposed ball conduit a formed in a plate 51a secured by screws 58a on a ilat face of the nut element, all to the end of providing a continuous ball race between the elements Si' and N' which is filled with balls ita providing an operative connection between the elements in the manner previously described.

the load, a camming action upon A single dog or pawl a is reciprcably mount- Y ed in abore in the nut element N', and is urged to the active position shown in Figure 6, by a coil spring Bla working in nut element', and bearing at one end against the head 93 of the pawl. and-at its other end against an adjustable pressure screw bore 92 and locked in adjusted position by a )am nut 95. Under the action of thespring "a, the working end of the n slot 66a in the ball conduit 56a into the path of movement of the balls therethough. The working end of the pawl is provided with a stop shoulder 96 to prevent circulation of the balls in the.

direction caused by the load. and is provided with a, cam -surface 91 to permit the balls to freely pass the pawl in the opposite direction caused by the driving force applied to the screw element in opposition to thev arrows in Figure 6.

Thus, the plunger 82 will be raised by utilizing the relatively small rolling friction of the freely circulating balls between the screw and nut elethe other in v an enlarged bore l2 of the j threaded in the pawl Bla projects through a.

load, `as is indicated by the` 1 elements-for relative .7 ments. and will be eifectivelysupported against lowering movement or retrograde driving of the mechanism by the largel sliding friction of noncirculating balls.

A release member in the form of a pull rod Illil,

extends through a longitudinal bore in the screw in the case oi an automobile jack.

It will be evident that by varying the shape of the stop shoulder 96 so that it presents a less abrupt steeply inclined surface to the balls 59a, and byvarying the loading of the spring 84a with the pressure screw 94, restricted circulation of the excessive loads. Under this condition, the stop shoulder 9B functions as an inclined cam surface I claim: 1;In mechanism of the* class described, two elements having co-acting helically related grooves; balls in said grooves operatively connecting said elements for relative movement, one g v by the other;

provide a means co-actlng with said grooves to support the load; and means co-acting with the balls to free them for rolling movement when necting said elements for relative movement, one by the other; means co-acting with said grooves to provide a continuous circulatory path along which thelballs are forced to roll in one `direction 8 forced to rollin' one direction or the other according as axial pressure is imposed in one direction or the other in said grooves opposite direction.

4. In mechanism of thel class described. two elements having co-acting heiically related grooves; balls in said opposition to a load, or in the other direction by the load; means co-acting with the balls to prevent circulation thereof in that direction caused imposed dn the load shocks.

5. In mechanism of the class 6. In mechanism of the class described, two

velements having mating helical grooves: balls in said grooves operatively connecting said elements to permit circulation of the balls in the reverse direction.

7. In mechanism of the class described, screw and nut elements having mating helical grooves;

elements forrelative movement, one by the other;

ball conduit in the nut element. co-acting with said grooves to provide a continupath along which the balls are forced to roll in one direction or the other according assaid relative movement of the elements is effected in one direction in opposition or in the other direction by the load;

said conduit; means urging said pawls to an active position wherein they respectively prevent circulation of the balls in opposite directions; andmeans lcio-acting with the pawls to maintain one inactive while the other is active, so as to permit circulation of the balls in the direction opposite to that-in which circulation of the balls is being preventedby the active pawl.l

8. In mechanism of the yclass described, screw and nut elements, the latter being composed of two sections operativelyconnected by a lost motion' rotational driving connection and for axial .movement as a unit; said screw element and one of said sections having mating helical grooves; balls in said groovesoperatively connecting said screw element and'said one section for relative axial moycmentl of the sections in response to relative rotation of the elements; means co-acting with said grooves to provide a continuous circulatory path along which the balls are forced to roll in one direction or the other according as said axial movement of the elements is effected and nut elements, the latter being composed of two sections operatively connected by a lost motion rotational 4driving connection and for axial movement as a unit; said screw element and one f of said sections having mating helical grooves;

balls in said grooves operatively connecting said screw element andsaid one section for relative axial movement of the sections in response to relative rotation of the elements; means co-acting with` said grooves to provide a continuous circulatory pathv along which the balls are forced to roll in one direction or the other according as said axial movement of the elements is effected in one direction or the other under load; two pawls; means urging said pawls to an active position wherein they respectively co-act with the balls in preventing circulation thereof in opposite directions; and means on said other nut section for moving one pawl or the other to an .inactive position according as the rotation between the elements permitted by said lost motion connection therebetween is effected in one direction or the other,

10. In mechanism of the class described, two elements having co-acting helically related grooves; balls in said grooves operatively connecting said elements for relative movement, one by the other: means co-acting with said grooves to provide a continuous circulatory path along which the balls are forced to roll in one direction or the other according as said relative movement of the elements is effected in opposition to a load, or in the other direction by the load; a pawl; means urging Isaid pawl to an active position wherein the pawl will co-act with the balls in preventing their circulation in that direction caused by the load, so as to utilize sliding friction of the balls between the elements, in supporting the load; and means by which said pawl can be moved to an inactiveposition so as to restore the rolling friction of the balls between the elements for retrograd Vmovement thereof by the load.

11. In mechanism of the class described, two elements, one of which is Ladapted to be driven for co-actionk with the other in moving a load; a series of balls; means defining a continuous race between said elements receivingsaid balls to operatively connect the elements for relative movement through the medium of the balls which are forced to circulate in one direction or the other according as said relative movement of the elements is effected in one direction in opposition to a load, or in the other direction by the load; a movably mounted pawl adapted to co-act with said balls; and means yieldingly uging said pawl to an :active position wherein said pawl will prevent circulation of the balls in one direction.

12. In mechanism of the class described, two elements, one of which is adapted to-be driven for co-action with the other in moving a load; a series of balls; means defining a continuous race between said elements receiving said balls to operatively connect the elements for relative movement through the medium of the balls which are forced -to circulate in one direction or the other according as said relative movement of the elements is effected in one direction in opposition to a load, or in the other direction by the load; a movably mounted pawl adaptd to co-act with said balls; and means yieldingly urging said pawl to an active position wherein said pawl will retard circulation of the balls in said other direction to a predetermined extent. yet render the balls relatively free to circulate in said one direction.

THEODORE W. VICKERS.

REFERENCES CITED UNITED STATES PATENTS Name Date Coughlan Oct. 4, 1898 Number

US2444886A 1945-04-09 1945-04-09 Screw and nut actuating mechanism Expired - Lifetime US2444886A (en)

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Cited By (34)

* Cited by examiner, † Cited by third party
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US2617308A (en) * 1950-12-04 1952-11-11 William H Kuntz Irreversible control linkage
US2623403A (en) * 1949-07-12 1952-12-30 Boeing Co Ball-bearing screw restraining mechanism
US2716537A (en) * 1949-06-08 1955-08-30 Gen Motors Corp Scissors jack
US2780943A (en) * 1950-09-27 1957-02-12 Daimler Benz Ag Motion-transmitting device, particularly for the steering mechanism of motor vehicles
US2836075A (en) * 1949-06-08 1958-05-27 Gen Motors Corp One-way ball nut
US2837182A (en) * 1957-08-12 1958-06-03 Southern Steel Co Keyless locking and operating systems for cell doors
US2855792A (en) * 1955-06-20 1958-10-14 Cleveland Pneumatic Ind Inc Ball screw and nut construction
US2857775A (en) * 1954-02-23 1958-10-28 Bendix Aviat Corp Holding brake for reversible screw jack
US2882742A (en) * 1955-10-14 1959-04-21 Cleveland Pneumatic Ind Inc Ball screw and nut construction
US2944169A (en) * 1956-07-05 1960-07-05 Abrams Instr Corp Motor and governor supporting assembly
US2956188A (en) * 1956-04-06 1960-10-11 Fostoria Corp Sealless motor for valve operation
US3042372A (en) * 1960-05-27 1962-07-03 Gen Motors Corp Powered jack screw assembly
US3153158A (en) * 1962-03-26 1964-10-13 Falk Corp Thru-motor drive
DE1208582B (en) * 1962-04-16 1966-01-05 Gen Motors Corp screw gear
US3399581A (en) * 1966-07-25 1968-09-03 Sargent Industries Ball nut and screw assembly
US3682283A (en) * 1970-03-02 1972-08-08 Mitumasa Sato Motor-driven actuator and safety overload mechanism therefor
US4352035A (en) * 1979-10-20 1982-09-28 Robert Bosch Gmbh Electric motor operated adjusting drive
US4500805A (en) * 1984-02-07 1985-02-19 Esco Design, Inc. Electromechanical linear actuator
US4579012A (en) * 1983-05-04 1986-04-01 Kollmorgen Technologies Corporation Compact electromechanical actuator
US4603594A (en) * 1984-05-31 1986-08-05 Sundstrand Corporation Fail safe actuator
US4604911A (en) * 1982-02-26 1986-08-12 Hiroshi Teramachi Recirculating-ball rotary-to-linear converter with an improved ball return guide
EP0258522A1 (en) * 1986-08-28 1988-03-09 Josef Pradler Linear-transmission unit
US4867000A (en) * 1986-11-10 1989-09-19 Lentz Dennis G Linear motion power cylinder
US5121019A (en) * 1986-08-26 1992-06-09 Josef Pradler Rotary to linear drive unit
DE4127487A1 (en) * 1991-08-20 1993-03-04 Harmonic Drive Antriebstechnik actuator
WO1999010662A1 (en) * 1997-08-22 1999-03-04 INA Wälzlager Schaeffler oHG Device for converting a rotary movement into a linear movement
NL1007296C2 (en) * 1997-10-16 1999-04-19 Skf Ind Trading & Dev Modular actuator, as well as a brake caliper having such an actuator.
US6453761B1 (en) 2000-11-16 2002-09-24 Thomson Saginaw Ball Screw Company, L.L.C. Direct attachment electric motor operated ball nut and screw linear actuator
US6603229B1 (en) * 2000-11-15 2003-08-05 Tri-Tech, Inc. Linear actuator with threaded captivation sleeve, captive lead screw, and spring pre-load adjustment
US20060221518A1 (en) * 2005-03-31 2006-10-05 Mark Evans Linear actuator
US20080196524A1 (en) * 2005-09-28 2008-08-21 Hans-Juergen Oberle Transmission Drive Unit With A Receiving Module, In Particular For Adjusting A Movable Part In A Motor Vehicle
EP2187097A1 (en) 2008-11-14 2010-05-19 Nozag AG Linear drive
US20100162838A1 (en) * 2008-12-26 2010-07-01 Nabtesco Corporation Electric actuator
US20140230584A1 (en) * 2012-10-31 2014-08-21 Goodrich Actuation Systems Limited Actuator Arrangement

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US611832A (en) * 1898-10-04 Jack-screw

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US611832A (en) * 1898-10-04 Jack-screw

Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2716537A (en) * 1949-06-08 1955-08-30 Gen Motors Corp Scissors jack
US2836075A (en) * 1949-06-08 1958-05-27 Gen Motors Corp One-way ball nut
US2623403A (en) * 1949-07-12 1952-12-30 Boeing Co Ball-bearing screw restraining mechanism
US2780943A (en) * 1950-09-27 1957-02-12 Daimler Benz Ag Motion-transmitting device, particularly for the steering mechanism of motor vehicles
US2617308A (en) * 1950-12-04 1952-11-11 William H Kuntz Irreversible control linkage
US2857775A (en) * 1954-02-23 1958-10-28 Bendix Aviat Corp Holding brake for reversible screw jack
US2855792A (en) * 1955-06-20 1958-10-14 Cleveland Pneumatic Ind Inc Ball screw and nut construction
US2882742A (en) * 1955-10-14 1959-04-21 Cleveland Pneumatic Ind Inc Ball screw and nut construction
US2956188A (en) * 1956-04-06 1960-10-11 Fostoria Corp Sealless motor for valve operation
US2944169A (en) * 1956-07-05 1960-07-05 Abrams Instr Corp Motor and governor supporting assembly
US2837182A (en) * 1957-08-12 1958-06-03 Southern Steel Co Keyless locking and operating systems for cell doors
US3042372A (en) * 1960-05-27 1962-07-03 Gen Motors Corp Powered jack screw assembly
US3153158A (en) * 1962-03-26 1964-10-13 Falk Corp Thru-motor drive
DE1208582B (en) * 1962-04-16 1966-01-05 Gen Motors Corp screw gear
US3399581A (en) * 1966-07-25 1968-09-03 Sargent Industries Ball nut and screw assembly
US3682283A (en) * 1970-03-02 1972-08-08 Mitumasa Sato Motor-driven actuator and safety overload mechanism therefor
US4352035A (en) * 1979-10-20 1982-09-28 Robert Bosch Gmbh Electric motor operated adjusting drive
US4604911A (en) * 1982-02-26 1986-08-12 Hiroshi Teramachi Recirculating-ball rotary-to-linear converter with an improved ball return guide
US4579012A (en) * 1983-05-04 1986-04-01 Kollmorgen Technologies Corporation Compact electromechanical actuator
US4500805A (en) * 1984-02-07 1985-02-19 Esco Design, Inc. Electromechanical linear actuator
US4603594A (en) * 1984-05-31 1986-08-05 Sundstrand Corporation Fail safe actuator
US5121019A (en) * 1986-08-26 1992-06-09 Josef Pradler Rotary to linear drive unit
EP0258522A1 (en) * 1986-08-28 1988-03-09 Josef Pradler Linear-transmission unit
US4867000A (en) * 1986-11-10 1989-09-19 Lentz Dennis G Linear motion power cylinder
DE4127487A1 (en) * 1991-08-20 1993-03-04 Harmonic Drive Antriebstechnik actuator
US5370011A (en) * 1991-08-20 1994-12-06 Harmonic Drive Antriebstechnik Gmbh Positioning actuator
WO1999010662A1 (en) * 1997-08-22 1999-03-04 INA Wälzlager Schaeffler oHG Device for converting a rotary movement into a linear movement
US6666308B1 (en) 1997-10-16 2003-12-23 Skf Engineering And Research Centre B.V. Modular actuator, and brake calliper comprising such actuator
WO1999021266A1 (en) * 1997-10-16 1999-04-29 Skf Engineering & Research Centre B.V. Modular actuator, and brake calliper comprising such actuator
NL1007296C2 (en) * 1997-10-16 1999-04-19 Skf Ind Trading & Dev Modular actuator, as well as a brake caliper having such an actuator.
US6603229B1 (en) * 2000-11-15 2003-08-05 Tri-Tech, Inc. Linear actuator with threaded captivation sleeve, captive lead screw, and spring pre-load adjustment
US6453761B1 (en) 2000-11-16 2002-09-24 Thomson Saginaw Ball Screw Company, L.L.C. Direct attachment electric motor operated ball nut and screw linear actuator
US20060221518A1 (en) * 2005-03-31 2006-10-05 Mark Evans Linear actuator
US7211971B2 (en) 2005-03-31 2007-05-01 Hitachi Automotive Products (Usa), Inc. Linear actuator
US20080196524A1 (en) * 2005-09-28 2008-08-21 Hans-Juergen Oberle Transmission Drive Unit With A Receiving Module, In Particular For Adjusting A Movable Part In A Motor Vehicle
US8033192B2 (en) * 2005-09-28 2011-10-11 Robert Bosch Gmbh Transmission drive unit with a receiving module for adjusting a movable part in a motor vehicle
EP2187097A1 (en) 2008-11-14 2010-05-19 Nozag AG Linear drive
US20100162838A1 (en) * 2008-12-26 2010-07-01 Nabtesco Corporation Electric actuator
US8505399B2 (en) * 2008-12-26 2013-08-13 Nabtesco Corporation Electric actuator
US9523416B2 (en) * 2012-10-31 2016-12-20 Goodrich Actuation Systems Limited Actuator arrangement
US20140230584A1 (en) * 2012-10-31 2014-08-21 Goodrich Actuation Systems Limited Actuator Arrangement

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